TWI745927B - Centrifugal heat dissipation fan - Google Patents

Centrifugal heat dissipation fan Download PDF

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Publication number
TWI745927B
TWI745927B TW109112338A TW109112338A TWI745927B TW I745927 B TWI745927 B TW I745927B TW 109112338 A TW109112338 A TW 109112338A TW 109112338 A TW109112338 A TW 109112338A TW I745927 B TWI745927 B TW I745927B
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Taiwan
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zone
flap
cooling fan
centrifugal cooling
air inlet
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TW109112338A
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Chinese (zh)
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TW202138687A (en
Inventor
陳宗廷
廖文能
謝錚玟
林育民
柯召漢
林光華
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宏碁股份有限公司
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Priority to TW109112338A priority Critical patent/TWI745927B/en
Priority to CN202010376222.9A priority patent/CN113530859B/en
Priority to US17/222,963 priority patent/US11629725B2/en
Publication of TW202138687A publication Critical patent/TW202138687A/en
Application granted granted Critical
Publication of TWI745927B publication Critical patent/TWI745927B/en

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    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04D—NON-POSITIVE-DISPLACEMENT PUMPS
    • F04D25/00—Pumping installations or systems
    • F04D25/02—Units comprising pumps and their driving means
    • F04D25/08—Units comprising pumps and their driving means the working fluid being air, e.g. for ventilation
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04D—NON-POSITIVE-DISPLACEMENT PUMPS
    • F04D29/00—Details, component parts, or accessories
    • F04D29/26—Rotors specially for elastic fluids
    • F04D29/28—Rotors specially for elastic fluids for centrifugal or helico-centrifugal pumps for radial-flow or helico-centrifugal pumps
    • F04D29/281—Rotors specially for elastic fluids for centrifugal or helico-centrifugal pumps for radial-flow or helico-centrifugal pumps for fans or blowers
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04D—NON-POSITIVE-DISPLACEMENT PUMPS
    • F04D29/00—Details, component parts, or accessories
    • F04D29/26—Rotors specially for elastic fluids
    • F04D29/28—Rotors specially for elastic fluids for centrifugal or helico-centrifugal pumps for radial-flow or helico-centrifugal pumps
    • F04D29/30—Vanes
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04D—NON-POSITIVE-DISPLACEMENT PUMPS
    • F04D17/00—Radial-flow pumps, e.g. centrifugal pumps; Helico-centrifugal pumps
    • F04D17/08—Centrifugal pumps
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04D—NON-POSITIVE-DISPLACEMENT PUMPS
    • F04D29/00—Details, component parts, or accessories
    • F04D29/08—Sealings
    • F04D29/16—Sealings between pressure and suction sides
    • F04D29/161—Sealings between pressure and suction sides especially adapted for elastic fluid pumps
    • F04D29/162—Sealings between pressure and suction sides especially adapted for elastic fluid pumps of a centrifugal flow wheel
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04D—NON-POSITIVE-DISPLACEMENT PUMPS
    • F04D29/00—Details, component parts, or accessories
    • F04D29/26—Rotors specially for elastic fluids
    • F04D29/28—Rotors specially for elastic fluids for centrifugal or helico-centrifugal pumps for radial-flow or helico-centrifugal pumps
    • F04D29/281—Rotors specially for elastic fluids for centrifugal or helico-centrifugal pumps for radial-flow or helico-centrifugal pumps for fans or blowers
    • F04D29/282—Rotors specially for elastic fluids for centrifugal or helico-centrifugal pumps for radial-flow or helico-centrifugal pumps for fans or blowers the leading edge of each vane being substantially parallel to the rotation axis
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04D—NON-POSITIVE-DISPLACEMENT PUMPS
    • F04D29/00—Details, component parts, or accessories
    • F04D29/40—Casings; Connections of working fluid
    • F04D29/42—Casings; Connections of working fluid for radial or helico-centrifugal pumps
    • F04D29/4206—Casings; Connections of working fluid for radial or helico-centrifugal pumps especially adapted for elastic fluid pumps
    • F04D29/4213—Casings; Connections of working fluid for radial or helico-centrifugal pumps especially adapted for elastic fluid pumps suction ports
    • G—PHYSICS
    • G06—COMPUTING; CALCULATING OR COUNTING
    • G06F—ELECTRIC DIGITAL DATA PROCESSING
    • G06F1/00—Details not covered by groups G06F3/00 - G06F13/00 and G06F21/00
    • G06F1/16—Constructional details or arrangements
    • G06F1/20—Cooling means
    • G06F1/203—Cooling means for portable computers, e.g. for laptops

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  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Theoretical Computer Science (AREA)
  • Computer Hardware Design (AREA)
  • Human Computer Interaction (AREA)
  • Physics & Mathematics (AREA)
  • General Physics & Mathematics (AREA)
  • Structures Of Non-Positive Displacement Pumps (AREA)

Abstract

A centrifugal heat dissipation fan including a housing and an impeller is provided. The housing has at least one flow inlet. The impeller assembled in the housing and rotating about an axial direction includes a hub and a plurality blades disposed around the hub. The flow inlet is located at the axial direction and facing the hub. Each of the blades has a wing tab next to the flow inlet, and the wing tab extends from a main surface of the blade to another blade. The wing tab has an inclined surface facing toward a surrounding edge of the flow inlet along a radial direction of the impeller.

Description

離心式散熱風扇Centrifugal cooling fan

本發明是有關於一種散熱風扇，且特別是有關於一種離心式散熱風扇。The present invention relates to a cooling fan, and more particularly to a centrifugal cooling fan.

一般而言，為了提升筆記型電腦內的散熱效果，不外乎採用降低系統熱阻或是提升其內散熱風扇的效能。然因筆記型電腦的外觀朝向輕薄化且不喜太多的散熱孔，因此導致系統熱阻較大，進而使散熱風扇的吸風量減少，而讓外部環境的空氣不易進入系統以產生散熱所需的熱對流。Generally speaking, in order to improve the heat dissipation effect in a notebook computer, it is nothing more than reducing the thermal resistance of the system or improving the performance of the cooling fan inside. However, because the appearance of the notebook is thinner and does not like too many heat dissipation holes, the thermal resistance of the system is larger, which reduces the air intake of the cooling fan, and makes it difficult for air from the external environment to enter the system to generate heat dissipation. Heat convection.

同時，現有離心式風扇的葉片之間氣隙較大，也因此不易控制氣流而容易造成回流，以致風壓不足，從而影響散熱效率。再者，一旦增大入風口而提高入風量的同時，若扇葉並未提供對應的結構，則也容易造成漏風等情形。At the same time, the existing centrifugal fan has a large air gap between the blades, and therefore it is not easy to control the airflow and easily cause backflow, resulting in insufficient wind pressure, which affects the heat dissipation efficiency. Moreover, once the air inlet is enlarged to increase the air inlet volume, if the fan blade does not provide a corresponding structure, it will easily cause air leakage and other situations.

據此，在現有系統熱阻已存在的情形下，勢必針對散熱風扇的風壓與風量提供有效地提升手段，方能有效解決上述問題。Accordingly, in the case where the thermal resistance of the existing system already exists, it is bound to provide an effective means for increasing the air pressure and air volume of the cooling fan, so as to effectively solve the above-mentioned problems.

本發明提供一種離心式散熱風扇，其藉由扇葉的葉型與殼體的入風口產生對應，以兼具高入風量與高風壓而能提高其散熱效能。The present invention provides a centrifugal heat dissipation fan, which can improve the heat dissipation efficiency by having the blade shape of the fan blade corresponding to the air inlet of the casing so as to have both high air inlet volume and high wind pressure.

本發明的離心式散熱風扇，包括殼體以及葉輪。殼體具有至少一入風口。葉輪沿一軸向可旋轉地組裝於殼體內，葉輪具有輪轂與環繞輪轂配置的多個扇葉，入風口位於軸向上且正對於輪轂。各扇葉具有相鄰於入風口的折翼，折翼從扇葉的葉面朝向相鄰的另一扇葉延伸，且折翼具有斜面，斜面沿葉輪的徑向而面對入風口的周緣。The centrifugal cooling fan of the present invention includes a casing and an impeller. The shell has at least one air inlet. The impeller is rotatably assembled in the casing along an axial direction. The impeller has a hub and a plurality of fan blades arranged around the hub. The air inlet is located in the axial direction and is facing the hub. Each fan blade has a folding wing adjacent to the air inlet, the folding wing extends from the blade surface of the fan blade to another adjacent fan blade, and the folding wing has an inclined surface that faces the periphery of the air inlet along the radial direction of the impeller .

基於上述，離心式散熱風扇藉由在扇葉鄰近入風口處形成折翼，且使折翼具有面對入風口周緣的斜面，如此一來，折翼的斜面還能與入風口搭配而形成將殼體外部的氣流引至殼體之內的導引結構，故而折翼的存在及其與入風口的適配性質能有效地提高離心式散熱風扇的入風量。同時，由於折翼的彎折方向是朝相鄰的另一扇葉延伸，因此對於葉輪整體而言，這些折翼將會對殼體的內部提供遮蔽效果，也就是讓已被吸入殼體內部的氣流能持續地被保留在殼體之內進行加壓，直至從出風口傳出。Based on the above, the centrifugal cooling fan is formed by forming a folding wing near the air inlet of the fan blade, and making the folding wing have an inclined surface facing the periphery of the air inlet. As a result, the inclined surface of the folding wing can also be matched with the air inlet to form a The airflow from the outside of the casing is guided to the guiding structure inside the casing, so the existence of the flaps and their adaptability to the air inlet can effectively increase the air intake of the centrifugal cooling fan. At the same time, since the bending direction of the flaps extends toward another adjacent blade, for the impeller as a whole, these flaps will provide a shielding effect on the inside of the casing, that is, let the inside of the casing have been sucked into it. The airflow can be kept in the shell continuously and pressurized until it passes out from the air outlet.

換句話說，現有將入風口予以擴大而欲導致的提高風量效果若搭配現有葉輪，則面臨到的即是上述漏風的情形會隨之產生，同時對殼體內的氣流加壓效果也有線。但，若改以搭配本發明的離心式散熱風扇的葉輪，則因應上述扇葉的折翼葉型特徵，便能提供將外部氣流導入殼體內的效果，也能有效地對殼體內的氣流進行加壓，以有效改善上述漏風的情形發生，並進而提高離心式散熱風扇的運作效率。In other words, if the existing air inlet is enlarged to increase the air volume effect, if it is matched with the existing impeller, the above-mentioned air leakage situation will occur, and the air pressure effect in the casing is also wired. However, if the impeller matching the centrifugal cooling fan of the present invention is used, it can provide the effect of introducing the external airflow into the casing in accordance with the characteristics of the above-mentioned fan blades, and can effectively control the airflow in the casing. Pressure is applied to effectively improve the occurrence of the above-mentioned air leakage, and further improve the operating efficiency of the centrifugal cooling fan.

圖1是依據本發明一實施例的離心式散熱風扇的***圖。圖2A是圖1的離心式散熱風扇的扇葉的立體視圖。圖2B是圖1的離心式散熱風扇的局部側視圖。在此同時提供直角座標X-Y-Z以利於構件描述。請同時參考圖1與圖2A、圖2B，在本實施例中，離心式散熱風扇100包括殼體120以及葉輪110。殼體120由基座122與頂板121構成，且殼體120具有入風口122a、121a。在此，殼體120的入風口121a、122a分屬於頂板121與基座122，而其中與葉輪110存在搭配關係者僅入風口121a，故後續將以入風口121a作為描述對象，但本發明並未以此為限。於另一未繪示的實施例中，葉輪也可使其扇葉的葉型與入風口122a進行搭配，而達到與本實施例相同之效果。換句話說，對於離心式散熱風扇100而言，其是以軸向L1入風而以徑向D1出風作為其運作模式，也就是在葉輪110運轉的狀態下，殼體120外部的氣流會經由入風口121a、122a進入殼體120，並經由出風口122b（頂板121與基座122相互結合而構成）被傳出殼體120，因而在此模式之下，使葉輪的扇葉搭配至少任一入風口，皆能產生與本實施例相同的效果。Fig. 1 is an exploded view of a centrifugal cooling fan according to an embodiment of the present invention. Fig. 2A is a perspective view of a fan blade of the centrifugal cooling fan of Fig. 1. Fig. 2B is a partial side view of the centrifugal cooling fan of Fig. 1. At the same time, right-angle coordinates X-Y-Z are provided to facilitate component description. Please refer to FIGS. 1 and 2A and 2B at the same time. In this embodiment, the centrifugal cooling fan 100 includes a casing 120 and an impeller 110. The housing 120 is composed of a base 122 and a top plate 121, and the housing 120 has air inlets 122a and 121a. Here, the air inlets 121a and 122a of the casing 120 belong to the top plate 121 and the base 122. Among them, the only one that has a matching relationship with the impeller 110 is the air inlet 121a. Therefore, the air inlet 121a will be used as the description object in the following, but the present invention does not Not limited by this. In another embodiment not shown, the impeller can also match the blade shape of the fan blade with the air inlet 122a to achieve the same effect as this embodiment. In other words, for the centrifugal cooling fan 100, it takes in the air in the axial direction L1 and discharges the air in the radial direction D1 as its operation mode. It enters the housing 120 through the air inlets 121a and 122a, and is passed out of the housing 120 through the air outlet 122b (the top plate 121 and the base 122 are combined with each other). Therefore, in this mode, the fan blades of the impeller can be matched at least freely. An air inlet can produce the same effect as this embodiment.

在本實施例中，葉輪110沿軸向L1可旋轉地組裝於殼體120內，所述軸向L1平行Z軸，葉輪110具有輪轂111與環繞輪轂111配置的多個扇葉112，入風口121a位於軸向L1上且正對於輪轂111。各扇葉112具有相鄰於入風口121a的折翼112a，折翼112a從扇葉112的葉面（main surface）朝向相鄰的另一扇葉112延伸，且折翼112a具有斜面V1，斜面V1沿葉輪110的徑向D1而面對入風口121a的周緣輪廓。In this embodiment, the impeller 110 is rotatably assembled in the housing 120 along the axial direction L1, which is parallel to the Z axis. The impeller 110 has a hub 111 and a plurality of fan blades 112 arranged around the hub 111, and an air inlet 121a is located on the axial direction L1 and is facing the hub 111. Each fan blade 112 has a flap 112a adjacent to the air inlet 121a. The flap 112a extends from the main surface of the fan blade 112 toward another adjacent fan blade 112, and the flap 112a has a slope V1. V1 faces the peripheral contour of the air inlet 121a along the radial direction D1 of the impeller 110.

圖3是圖1的離心式散熱風扇的扇葉的俯視圖。請同時參考圖2A、圖2B與圖3，在本實施例中，扇葉112沿徑向D1區分為第一區A1、第二區A2與第三區A3，第一區A1連接輪轂111，第二區A2連接在第一區A1與第三區A3之間，折翼112a從第二區A2延伸出，並相對於扇葉112的葉面呈現彎折，且較佳呈現的彎折角為90度。在此，第二區A2沿軸向L1的尺寸大於第一區A1沿軸向L1的尺寸，且第二區A2沿軸向L1的尺寸大於第三區A3沿軸向L1的尺寸。換句話說，僅以單一扇葉112而言，折翼112a所在的第二區A2，其具有較扇葉112的第一區A1、第三區A3為高的狀態，亦即代表扇葉112在第二區A2處具有較大的葉面尺寸。此舉也相當於，相較於現有近乎等尺寸葉面的扇葉，本實施例的扇葉112的折翼112a實質上應建立在具有較大葉面的局部以利於靠近入風口121a，也就是讓扇葉112的局部葉面沿軸向L1擴增之後，再於其上形成折翼112a。圖2B保壓，風不易出。Fig. 3 is a plan view of a blade of the centrifugal cooling fan of Fig. 1. Please refer to FIGS. 2A, 2B and 3 at the same time. In this embodiment, the fan blade 112 is divided into a first area A1, a second area A2, and a third area A3 along the radial direction D1. The first area A1 is connected to the hub 111, The second area A2 is connected between the first area A1 and the third area A3, and the flap 112a extends from the second area A2 and is bent relative to the blade surface of the fan blade 112, and the preferred bending angle is 90 degrees. Here, the size of the second zone A2 in the axial direction L1 is larger than the size of the first zone A1 in the axial direction L1, and the size of the second zone A2 in the axial direction L1 is larger than the size of the third zone A3 in the axial direction L1. In other words, for a single fan blade 112, the second area A2 where the flap 112a is located has a higher state than the first area A1 and the third area A3 of the fan blade 112, which means that the fan blade 112 is represented. There is a larger leaf size in the second area A2. This action is also equivalent to that, compared with the existing fan blades with nearly equal-sized blade surfaces, the folding wings 112a of the fan blade 112 in this embodiment should essentially be built on a part with a larger blade surface so as to be close to the air inlet 121a, that is, After the partial leaf surface of the fan blade 112 is enlarged along the axial direction L1, a flap 112a is formed thereon. Figure 2B maintains pressure, the wind is not easy to come out.

進一步地說，將本實施例的葉輪110整體觀之，其多個扇葉112實質上座落在同一個平面BS，且本實施例的平面BS平行於X-Y平面，並使前述軸向L1成為平面BS的法線。這些扇葉112在此情形下，其第二區A2的頂部相對於平面BS的高度h1、h2大於第一區A1的頂部相對於平面BS的高度h3，且第二區A2的頂部相對於平面BS的高度h1、h2也會大於第三區A3的頂部相對於平面BS的高度h4，如圖2B所示，也就是說，具有折翼112a的第二區A2，其相較於第一區A1與第三區A3要更為接近入風口121a的周緣，進而在葉輪110運轉時能造成殼體120外部的氣流F1因入風口121a與折翼112a的斜面V1所形成的通道結構而被順利地導引至殼體120內。Furthermore, in an overall view of the impeller 110 of this embodiment, its multiple fan blades 112 are substantially located on the same plane BS, and the plane BS of this embodiment is parallel to the XY plane, and the aforementioned axial direction L1 becomes a plane. The normal of BS. In this case, the heights h1, h2 of the top of the second area A2 relative to the plane BS of the fan blades 112 are greater than the height h3 of the top of the first area A1 relative to the plane BS, and the top of the second area A2 is relative to the plane The heights h1 and h2 of the BS will also be greater than the height h4 of the top of the third zone A3 relative to the plane BS, as shown in FIG. The A1 and the third area A3 are closer to the periphery of the air inlet 121a, and when the impeller 110 is running, the airflow F1 outside the casing 120 can be smoothed due to the channel structure formed by the air inlet 121a and the inclined surface V1 of the flap 112a. The ground is guided into the housing 120.

再者，於本實施例中，折翼112a相對於平面BS的高度是沿徑向D1而逐漸降低。請同時參考圖2B與圖3，折翼112a相對於輪轂111的旋轉中心（也就是前述軸向L1）而在徑向D1上存在外徑R2與內徑R1（在此以軸向L1為基準，繪示折翼112a在徑向D1上的兩端處的半徑作為例示），且外徑R2大於內徑R1，對應至圖2即能清楚得知，外徑R2對應的高度h2小於內徑R1對應的高度h1，且是從內徑R1處逐漸往外徑R2處減少，其中內徑R1小於入風口121a的半徑R3，且入風口121a的半徑R3小於折翼112a的外徑R2，也就是折翼112a的局部被頂板121所遮蔽，以此尺寸搭配而形成斜面V1，且使斜面V1能與入風口121a形成導入氣流F1的通道結構。同時，也因折翼112a與入風口121a具備上述對應關係，因而對離心式散熱風扇100而言，其能使殼體120內的氣流不易外漏，而具備風壓維持效果。Furthermore, in this embodiment, the height of the flap 112a relative to the plane BS gradually decreases along the radial direction D1. 2B and 3 at the same time, the flap 112a has an outer diameter R2 and an inner diameter R1 in the radial direction D1 relative to the rotation center of the hub 111 (that is, the aforementioned axial direction L1) (here, the axial direction L1 is taken as the reference , The radius of the two ends of the flap 112a in the radial direction D1 is shown as an example), and the outer diameter R2 is greater than the inner diameter R1. Corresponding to Figure 2, it can be clearly seen that the height h2 corresponding to the outer diameter R2 is smaller than the inner diameter R1 corresponds to the height h1, and gradually decreases from the inner diameter R1 to the outer diameter R2, where the inner diameter R1 is smaller than the radius R3 of the air inlet 121a, and the radius R3 of the air inlet 121a is smaller than the outer diameter R2 of the flap 112a, that is Part of the flap 112a is shielded by the top plate 121, and the size is matched to form an inclined surface V1, and the inclined surface V1 and the air inlet 121a can form a channel structure for introducing the airflow F1. At the same time, because the flap 112a and the air inlet 121a have the above-mentioned corresponding relationship, for the centrifugal cooling fan 100, it can prevent the airflow in the housing 120 from leaking, and has the effect of maintaining wind pressure.

圖4A與圖4B分別是本發明不同實施例的離心式散熱風扇的局部側視圖。請先參考圖4A，與前述實施例不同的是，折翼112a的外徑R2小於入風口121a的半徑R4，亦即折翼112a完全從入風口121a暴露出，然入風口121a仍與折翼112a的斜面V1形成由殼體120外部朝向殼體120內部的漸縮輪廓，因此在殼體120的出風口122b（繪示於圖1）或其鄰近處，仍能因殼體120的內部氣流被排出而順利地將外部的氣流F1經由入風口121a導入殼體120，藉以增加離心式散熱風扇100的入風量。4A and 4B are partial side views of centrifugal cooling fans according to different embodiments of the present invention. Please refer to FIG. 4A first. The difference from the previous embodiment is that the outer diameter R2 of the flap 112a is smaller than the radius R4 of the air inlet 121a, that is, the flap 112a is completely exposed from the air inlet 121a, but the air inlet 121a is still connected to the flap The slope V1 of 112a forms a tapered profile from the outside of the housing 120 toward the inside of the housing 120. Therefore, the air outlet 122b (shown in FIG. 1) of the housing 120 or its vicinity can still be caused by the airflow inside the housing 120. The discharged airflow F1 is smoothly introduced into the casing 120 via the air inlet 121a, thereby increasing the air inlet volume of the centrifugal cooling fan 100.

請參考圖4B，其與前述實施例不同的是，折翼112a相對於平面BS的高度大於入風口121a相對於平面BS的高度，如圖所示折翼112a相對於頂板121存在突出間距G1，而此舉能進一步地增大入風量與風壓。換句話說，本實施例的扇葉412是讓其第二區A21進一步沿軸向L1擴展葉面，而使折翼112a得以突出於入風口121a，然與前述實施例不變的是，折翼112a的斜面V1仍能與入風口121a的周緣相互對應以形成漸縮輪廓，而同樣有利於將殼體120的外部氣流F1導引入殼體120。Please refer to FIG. 4B, which is different from the previous embodiment in that the height of the flap 112a relative to the plane BS is greater than the height of the air inlet 121a relative to the plane BS. As shown in the figure, the flap 112a has a protrusion distance G1 relative to the top plate 121. And this can further increase the inlet air volume and wind pressure. In other words, the fan blade 412 of this embodiment allows the second area A21 to further expand the blade surface along the axial direction L1, so that the flap 112a can protrude from the air inlet 121a. However, the same as the previous embodiment is that the folding The inclined surface V1 of the wing 112a can still correspond to the periphery of the air inlet 121a to form a tapered profile, and it is also beneficial to guide the external airflow F1 of the housing 120 into the housing 120.

基於上述實施例，總的來說，本發明的葉輪110在其扇葉112或412的第二區A2或A21沿軸向L1擴展，以讓其上的折翼112a得以鄰近入風口121a，並進而使折翼112a的斜面V1得以與入風口121a的周緣接近而形成漸縮輪廓，藉以提昇離心式散熱風扇100的入風量與風壓。同時，折翼112a沿徑向D1所具有的外徑R2及內徑R1，而讓設計者能據以調整至所需的入風量與風壓。在此，離心式散熱風扇100的入風量正比於內徑R1，離心式散熱風扇100的風壓反比於內徑R1。簡單的說，請參考圖3，當折翼112a的內徑R1越小時，代表折翼112a的徑向尺寸越大，如圖所示內徑R5，其相當於新增了如斜線所繪示的區域，對於殼體120的內部空間而言，上述形成的折翼112b相當於增加了遮蔽內部空間的面積，也提高對內部空間的氣流的保持率，如此便能提高離心式散熱風扇100的風壓。Based on the above-mentioned embodiment, in general, the impeller 110 of the present invention expands along the axial direction L1 in the second zone A2 or A21 of the fan blade 112 or 412, so that the flap 112a on it can be adjacent to the air inlet 121a, and Furthermore, the inclined surface V1 of the flap 112a can be close to the periphery of the air inlet 121a to form a tapered profile, so as to increase the air inlet volume and wind pressure of the centrifugal cooling fan 100. At the same time, the outer diameter R2 and the inner diameter R1 of the flap 112a along the radial direction D1 allow the designer to adjust the required air inlet volume and wind pressure accordingly. Here, the inlet air volume of the centrifugal cooling fan 100 is proportional to the inner diameter R1, and the wind pressure of the centrifugal cooling fan 100 is inversely proportional to the inner diameter R1. Simply put, please refer to Figure 3. When the inner diameter R1 of the flap 112a is smaller, the radial dimension of the flap 112a is larger. As shown in the figure, the inner diameter R5 is equivalent to the addition of For the internal space of the housing 120, the above-mentioned folded wings 112b are equivalent to increasing the area that shields the internal space, and also improves the airflow retention rate of the internal space, so that the centrifugal cooling fan 100 can be improved Wind pressure.

在本實施例的離心式散熱風扇100中，其入風口121a的直徑小於輪葉110的直徑，且以入風口121a的直徑是以葉輪110的直徑的80%為例，在此基礎上，若搭配以現有技術的葉輪，則當欲進一步增大入風量而加大入風口時，便會面臨到葉輪的扇葉無法配合而導致漏風情形產生。反之，若搭配本發明上述實施例的葉輪110，即其扇葉112或412是具有折翼112a者，則可望進一步縮減葉輪110與殼體120在入風口121a處的間距。換句話說，本發明的葉輪110藉由扇葉112或412上的折翼112a，而使原本的固定式遮蔽結構（即頂板121在入風口121a周緣的局部實體）改為活動式的遮蔽結構（即折翼112a），以在擴大入風口而提高入風量的同時也能兼具所需的風壓。類似地，即使毋須擴大入風口，具有折翼112a的扇葉112也能達到加大入風量與風壓的效果。In the centrifugal cooling fan 100 of this embodiment, the diameter of the air inlet 121a is smaller than the diameter of the vane 110, and the diameter of the air inlet 121a is 80% of the diameter of the impeller 110 as an example. On this basis, if With the impeller of the prior art, when the air inlet is to be further increased and the air inlet is enlarged, the fan blades of the impeller cannot be matched, resulting in air leakage. Conversely, if the impeller 110 of the above embodiment of the present invention is used, that is, the fan blade 112 or 412 has a flap 112a, it is expected to further reduce the distance between the impeller 110 and the casing 120 at the air inlet 121a. In other words, the impeller 110 of the present invention uses the flap 112a on the fan blade 112 or 412 to change the original fixed shielding structure (that is, the partial entity of the top plate 121 at the periphery of the air inlet 121a) to a movable shielding structure (I.e., the flap 112a), in order to expand the air inlet and increase the air volume, but also have the required wind pressure. Similarly, even if there is no need to expand the air inlet, the fan blade 112 with the flap 112a can achieve the effect of increasing the air inlet volume and wind pressure.

圖5A是本發明另一實施例的離心式散熱風扇的示意圖。圖5B以另一視角繪示圖5A的離心式散熱風扇的局部。請同時參考圖5A與圖5B，在本實施例的葉輪210中，各扇葉212的折翼212a從扇葉212的葉面朝向相鄰的另一扇葉212延伸並連接至所述另一扇葉212的另一折翼212a，以使葉輪210的這些折翼212a彼此連接而呈環形，而呈環形的折翼212a也同樣具有斜面V2以對應朝向殼體120的入風口121a（繪示於圖1），因而在能達到前述實施例相同的效果的同時，葉輪210也因此能有效提高其結構強度。在此並未限制折翼212a的連接形式，其可藉由金屬扇葉於沖壓過程中形成的扣件而逐一扣接，也可藉由模內射出而以塑膠材料銜接起這些扇葉212所形成。當然，扇葉212即其折翼212a也可皆由塑膠材料以一次性射出成型而完成。Fig. 5A is a schematic diagram of a centrifugal cooling fan according to another embodiment of the present invention. FIG. 5B shows a part of the centrifugal cooling fan of FIG. 5A from another perspective. Referring to FIGS. 5A and 5B at the same time, in the impeller 210 of this embodiment, the flap 212a of each fan blade 212 extends from the blade surface of the fan blade 212 toward another adjacent fan blade 212 and is connected to the other fan blade 212. The other flap 212a of the fan blade 212 connects the flaps 212a of the impeller 210 to form an annular shape, and the annular flap 212a also has a slope V2 to correspond to the air inlet 121a facing the housing 120 (shown As shown in FIG. 1), while achieving the same effect as the foregoing embodiment, the impeller 210 can also effectively improve its structural strength. The connection form of the flaps 212a is not limited here. It can be buckled one by one by the fasteners formed by the metal fan blades in the stamping process, or can be injected into the mold to connect the fan blades 212 with plastic materials. form. Of course, the fan blade 212, that is, its flap 212a, can also be formed by one-time injection molding of plastic materials.

圖6是本發明另一實施例的離心式散熱風扇的示意圖。請參考圖6，本實施例的葉輪310中，配置於輪轂111的扇葉312已具備前述實施例的相關特徵，例如彼此相鄰的折翼312a相互鄰接而呈環狀，且其同樣具有對應入風口121a的斜面V3，而不同的是，本實施例的扇葉312還具有破折葉緣312c與另一折翼312b，其中破折葉緣312c實質上位於扇葉312的第三區A3（如圖2A、圖2B所示），折翼312b與破折葉緣312c分別處於第三區A3的不同邊緣（破折葉緣312c鄰接在一對折翼312b之間），其中折翼312b相對於葉輪310的旋轉方向（如圖所示逆時針箭號）而呈後掠設計。在此，扇葉312與破折葉緣312c、折翼312b是由金屬板件沖壓、彎折而成。據此，本實施例的扇葉312除保有前述實施例的特徵與效果外，所述折翼312b與破折葉緣312c還能進一步地將扇葉312末端形成的渦流予以分散且弱化，以降低扇葉312旋轉對周遭空氣造成的擾動，進而達到提高運作效率及降噪的效果。Fig. 6 is a schematic diagram of a centrifugal cooling fan according to another embodiment of the present invention. Please refer to FIG. 6, in the impeller 310 of this embodiment, the fan blades 312 arranged on the hub 111 already have the relevant features of the previous embodiment, for example, the adjacent flaps 312a are adjacent to each other to form a ring shape, and they also have corresponding features. The difference is that the fan blade 312 of the present embodiment also has a broken blade edge 312c and another folding wing 312b. The broken blade edge 312c is substantially located in the third area A3 of the fan blade 312. (As shown in Figures 2A and 2B), the flaps 312b and the broken leaf edge 312c are located at different edges of the third area A3 (the broken leaf edge 312c is adjacent to a pair of flaps 312b), wherein the flaps 312b are opposite In the direction of rotation of the impeller 310 (counterclockwise arrow as shown in the figure), it is designed to be swept backward. Here, the fan blade 312, the broken blade edge 312c, and the folding wings 312b are formed by stamping and bending sheet metal parts. Accordingly, in addition to retaining the features and effects of the aforementioned embodiment, the fan blade 312 of this embodiment can further disperse and weaken the vortex formed at the end of the fan blade 312 by the flaps 312b and the broken blade edge 312c. The disturbance of the surrounding air caused by the rotation of the fan blade 312 is reduced, thereby achieving the effect of improving operation efficiency and reducing noise.

綜上所述，在本發明的上述實施例中，離心式散熱風扇藉由在扇葉鄰近入風口處形成折翼，且使折翼具有面對入風口周緣的斜面，如此一來，折翼的斜面還能與入風口搭配而形成將殼體外部的氣流引至殼體之內的導引結構，故而折翼的存在及其與入風口的適配性質能有效地提高離心式散熱風扇的入風量。同時，由於折翼的彎折方向是朝相鄰的另一扇葉延伸，因此對於葉輪整體而言，這些折翼將會對殼體的內部提供遮蔽效果，也就是讓已被吸入殼體內部的氣流能持續地被保留在殼體之內進行加壓，直至從出風口傳出。此外，設計者可針對所需入風量與風壓的不同需求而對應調整折翼的內徑尺寸、外徑尺寸，以及折翼相對於扇葉所在平面的高度。To sum up, in the above-mentioned embodiment of the present invention, the centrifugal cooling fan forms a flap near the air inlet of the fan blade, and the flap has a slope facing the periphery of the air inlet. In this way, the flap The inclined surface can also be matched with the air inlet to form a guiding structure that guides the airflow from the outside of the shell to the inside of the shell. Therefore, the existence of the flap and the adaptability of the air inlet can effectively improve the performance of the centrifugal cooling fan. Into the air volume. At the same time, since the bending direction of the flaps extends toward another adjacent blade, for the impeller as a whole, these flaps will provide a shielding effect on the inside of the casing, that is, let the inside of the casing have been sucked into it. The airflow can be kept in the shell continuously and pressurized until it passes out from the air outlet. In addition, the designer can adjust the inner diameter, outer diameter, and height of the flap relative to the plane where the fan blade is located according to the different requirements of the required air intake and wind pressure.

換句話說，現有將入風口予以擴大而欲導致的提高風量效果若搭配現有葉輪，則面臨到的即是上述漏風的情形會隨之產生，同時對殼體內的氣流加壓效果也有線。但，若改以搭配本發明的離心式散熱風扇的葉輪，則因應上述扇葉的折翼葉型特徵，便能提供將外部氣流導入殼體內的效果，也能有效地對殼體內的氣流進行加壓，以有效改善上述漏風的情形發生，並進而提高離心式散熱風扇的運作效率。In other words, if the existing air inlet is enlarged to increase the air volume effect, if it is matched with the existing impeller, the above-mentioned air leakage situation will occur, and the air pressure effect in the casing is also wired. However, if the impeller matching the centrifugal cooling fan of the present invention is used, it can provide the effect of introducing the external airflow into the casing in accordance with the characteristics of the above-mentioned fan blades, and can effectively control the airflow in the casing. Pressure is applied to effectively improve the occurrence of the above-mentioned air leakage, and further improve the operating efficiency of the centrifugal cooling fan.

100:離心式散熱風扇 110、210、310:葉輪 111:輪轂 112、212、312、412:扇葉 112a、112b、212a、312a:折翼 120:殼體 121:頂板 121a、122a:入風口 122b:出風口 122:基座 312b:折翼 312c:破折葉緣 A1:第一區 A2、A21:第二區 A3:第三區 BS:平面 D1:徑向 F1:氣流 G1:突出間距 h1、h2、h3、h4:高度 L1:軸向 R1、R5:內徑 R2:外徑 R3、R4:半徑 V1、V2、V3:斜面 X-Y-Z:直角座標 100: Centrifugal cooling fan 110, 210, 310: impeller 111: Wheel Hub 112, 212, 312, 412: fan blades 112a, 112b, 212a, 312a: folding wings 120: shell 121: top plate 121a, 122a: air inlet 122b: air outlet 122: Pedestal 312b: Folding Wing 312c: Broken Leaf Edge A1: Zone 1 A2, A21: Zone 2 A3: Zone 3 BS: Plane D1: radial F1: Airflow G1: prominent spacing h1, h2, h3, h4: height L1: axial R1, R5: inner diameter R2: Outer diameter R3, R4: radius V1, V2, V3: inclined plane X-Y-Z: Right-angle coordinates

圖1是依據本發明一實施例的離心式散熱風扇的***圖。 圖2A是圖1的離心式散熱風扇的扇葉的立體視圖。 圖2B是圖1的離心式散熱風扇的局部側視圖。 圖3是圖1的離心式散熱風扇的扇葉的俯視圖。 圖4A與圖4B分別是本發明不同實施例的離心式散熱風扇的局部側視圖。 圖5A是本發明另一實施例的離心式散熱風扇的示意圖。 圖5B以另一視角繪示圖5A的離心式散熱風扇的局部。 圖6是本發明另一實施例的離心式散熱風扇的示意圖。 Fig. 1 is an exploded view of a centrifugal cooling fan according to an embodiment of the present invention. Fig. 2A is a perspective view of a fan blade of the centrifugal cooling fan of Fig. 1. Fig. 2B is a partial side view of the centrifugal cooling fan of Fig. 1. Fig. 3 is a plan view of a blade of the centrifugal cooling fan of Fig. 1. 4A and 4B are partial side views of centrifugal cooling fans according to different embodiments of the present invention. Fig. 5A is a schematic diagram of a centrifugal cooling fan according to another embodiment of the present invention. FIG. 5B shows a part of the centrifugal cooling fan of FIG. 5A from another perspective. Fig. 6 is a schematic diagram of a centrifugal cooling fan according to another embodiment of the present invention.

100:離心式散熱風扇 110:葉輪 111:輪轂 112:扇葉 112a:折翼 120:殼體 121:頂板 121a、122a:入風口 122b:出風口 122:基座 D1:徑向 V1:斜面 X-Y-Z:直角座標 100: Centrifugal cooling fan 110: impeller 111: Wheel Hub 112: fan blade 112a: folding wings 120: shell 121: top plate 121a, 122a: air inlet 122b: air outlet 122: Pedestal D1: radial V1: inclined plane X-Y-Z: Right-angle coordinates

Claims (13)

一種離心式散熱風扇，包括： 一殼體，具有至少一入風口；以及 一葉輪，沿一軸向可旋轉地組裝於該殼體內，該葉輪具有一輪轂與環繞該輪轂配置的多個扇葉，該入風口位於該軸向上且正對於該輪轂，各該扇葉具有相鄰於該入風口的一折翼，該折翼從該扇葉的葉面朝向相鄰的另一扇葉延伸，且該折翼具有一斜面，該斜面沿該葉輪的一徑向而面對該入風口的周緣。 A centrifugal cooling fan includes: A shell with at least one air inlet; and An impeller is rotatably assembled in the housing along an axial direction. The impeller has a hub and a plurality of fan blades arranged around the hub. The air inlet is located in the axial direction and is opposite to the hub, and each fan blade has A flap adjacent to the air inlet, the flap extends from the blade surface of the fan blade toward another adjacent fan blade, and the flap has an inclined surface that faces along a radial direction of the impeller To the periphery of the air inlet. 如請求項1所述的離心式散熱風扇，其中該入風口的直徑小於該葉輪的直徑。The centrifugal cooling fan according to claim 1, wherein the diameter of the air inlet is smaller than the diameter of the impeller. 如請求項1所述的離心式散熱風扇，其中該扇葉沿該徑向區分為一第一區、一第二區與一第三區，該第一區連接該輪轂，該第二區連接在該第一區與該第三區之間，該折翼從該第二區延伸出。The centrifugal cooling fan according to claim 1, wherein the fan blade is divided into a first zone, a second zone and a third zone along the radial direction, the first zone is connected to the hub, and the second zone is connected to Between the first zone and the third zone, the flap extends from the second zone. 如請求項3所述的離心式散熱風扇，其中該第二區沿該軸向的尺寸大於該第一區沿該軸向的尺寸，且該第二區沿該軸向的尺寸大於該第三區沿該軸向的尺寸。The centrifugal cooling fan according to claim 3, wherein the size of the second zone in the axial direction is larger than the size of the first zone in the axial direction, and the size of the second zone in the axial direction is larger than that of the third zone The size of the zone along the axis. 如請求項3所述的離心式散熱風扇，其中該些扇葉座落於同一平面，該第二區的頂部相對於該平面的高度大於該第一區的頂部相對於該平面的高度，且該第二區的頂部相對於該平面的高度大於該第三區的頂部相對於該平面的高度。The centrifugal cooling fan according to claim 3, wherein the fan blades are located on the same plane, the height of the top of the second zone relative to the plane is greater than the height of the top of the first zone relative to the plane, and The height of the top of the second zone relative to the plane is greater than the height of the top of the third zone relative to the plane. 如請求項5所述的離心式散熱風扇，其中該折翼相對於該平面的高度沿該徑向而降低。The centrifugal cooling fan according to claim 5, wherein the height of the flap relative to the plane is reduced along the radial direction. 如請求項5所述的離心式散熱風扇，其中該折翼相對於該平面的高度大於該入風口相對於該平面的高度。The centrifugal cooling fan according to claim 5, wherein the height of the flap relative to the plane is greater than the height of the air inlet relative to the plane. 如請求項3所述的離心式散熱風扇，其中該第三區遠離該輪轂的一端還具有一破折葉緣。The centrifugal cooling fan according to claim 3, wherein the end of the third zone away from the hub further has a broken blade edge. 如請求項8所述的離心式散熱風扇，其中該第三區還具有至少一另一折翼，所述另一折翼與該破折葉緣分別處於該第三區的不同邊緣，所述另一折翼相對於該葉輪的旋轉方向而呈後掠設計。The centrifugal cooling fan according to claim 8, wherein the third zone further has at least one other flap, and the other flap and the broken blade edge are respectively located at different edges of the third zone, the The other flap is designed to be swept back relative to the direction of rotation of the impeller. 如請求項1所述的離心式散熱風扇，其中該折翼沿該徑向具有一外徑與一內徑，該外徑大於該內徑，該內徑小於該入風口的半徑，且該入風口的半徑小於該外徑。The centrifugal cooling fan according to claim 1, wherein the flap has an outer diameter and an inner diameter along the radial direction, the outer diameter is larger than the inner diameter, the inner diameter is smaller than the radius of the air inlet, and the inlet The radius of the tuyere is smaller than the outer diameter. 如請求項1所述的離心式散熱風扇，其中該折翼沿該徑向具有一外徑與一內徑，該外徑大於該內徑，且該外徑小於該入風口的半徑。The centrifugal cooling fan according to claim 1, wherein the flap has an outer diameter and an inner diameter along the radial direction, the outer diameter is larger than the inner diameter, and the outer diameter is smaller than the radius of the air inlet. 如請求項1所述的離心式散熱風扇，其中該折翼沿該徑向具有一外徑與一內徑，該外徑大於該內徑，該離心式散熱風扇的入風量正比於該內徑，該離心式散熱風扇的風壓反比於該內徑。The centrifugal cooling fan according to claim 1, wherein the flap has an outer diameter and an inner diameter along the radial direction, the outer diameter is larger than the inner diameter, and the air intake volume of the centrifugal cooling fan is proportional to the inner diameter , The wind pressure of the centrifugal cooling fan is inversely proportional to the inner diameter. 如請求項1所述的離心式散熱風扇，其中該折翼從該扇葉的葉面朝向相鄰的另一扇葉延伸並連接至所述另一扇葉的另一折翼，以使該葉輪的該些折翼彼此連接而呈環形。The centrifugal cooling fan according to claim 1, wherein the flap extends from the blade surface of the fan blade toward another adjacent fan blade and is connected to another flap of the other fan blade, so that the The flaps of the impeller are connected to each other to form a ring shape.
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Citations (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
TWI663339B (en) * 2017-10-26 2019-06-21 宏碁股份有限公司 Heat dissipation fan

Family Cites Families (13)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
ES2153282B1 (en) * 1998-06-09 2001-09-01 Escola Del Trebal Del Ripolles RODETE FOR FANS.
JP4432474B2 (en) * 2003-11-27 2010-03-17 ダイキン工業株式会社 Centrifugal blower impeller and centrifugal blower provided with the impeller
TW200521333A (en) * 2004-12-08 2005-07-01 Asia Vital Components Co Ltd Blade unit of centrifugal fan
CN1966993A (en) * 2005-11-16 2007-05-23 奇鋐科技股份有限公司 Fan blade unit for centrifugal fan
JP4631867B2 (en) * 2006-11-30 2011-02-16 パナソニック株式会社 Centrifugal fan device and electronic device including the same
US20080130226A1 (en) * 2006-11-30 2008-06-05 Matsushita Electric Industrial Co., Ltd. Centrifugal fan device and electronic apparatus having the same
TW200939938A (en) 2008-03-07 2009-09-16 Forcecon Technology Co Ltd Blade structure of centrifugal heat dissipation fan
CN102959249B (en) * 2010-06-30 2015-09-23 爱信精机株式会社 Impeller and manufacture method thereof
CN104033419B (en) * 2013-03-05 2016-08-10 建准电机工业股份有限公司 Impeller manufacture method
TWI487475B (en) 2013-04-02 2015-06-01 Quanta Comp Inc Heat dissipation module
CN206346936U (en) * 2016-12-30 2017-07-21 华硕电脑股份有限公司 Centrifugal fan
JP2018193892A (en) * 2017-05-15 2018-12-06 日本電産株式会社 Blowing apparatus
CN109751280B (en) * 2017-11-07 2021-10-22 宏碁股份有限公司 Heat radiation fan

Patent Citations (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
TWI663339B (en) * 2017-10-26 2019-06-21 宏碁股份有限公司 Heat dissipation fan

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